EP0299324B1 - Raccord de tuyau télémanipulable et outil multifonctionnel pour celui-ci - Google Patents

Raccord de tuyau télémanipulable et outil multifonctionnel pour celui-ci Download PDF

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Publication number
EP0299324B1
EP0299324B1 EP88110663A EP88110663A EP0299324B1 EP 0299324 B1 EP0299324 B1 EP 0299324B1 EP 88110663 A EP88110663 A EP 88110663A EP 88110663 A EP88110663 A EP 88110663A EP 0299324 B1 EP0299324 B1 EP 0299324B1
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EP
European Patent Office
Prior art keywords
tube connection
screw
connection according
screwthread
flange
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP88110663A
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German (de)
English (en)
Other versions
EP0299324A1 (fr
Inventor
Hans-Peter Dipl.-Ing. Schabert
Erich Strickroth
Erwin Dipl.-Ing. Laurer (Fh)
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Deutsche Gesellschaft fuer Wiederaufarbeitung von Kernbrennstoffen mbH
Original Assignee
Deutsche Gesellschaft fuer Wiederaufarbeitung von Kernbrennstoffen mbH
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Publication of EP0299324A1 publication Critical patent/EP0299324A1/fr
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Publication of EP0299324B1 publication Critical patent/EP0299324B1/fr
Anticipated expiration legal-status Critical
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
    • F16B35/00—Screw-bolts; Stay-bolts; Screw-threaded studs; Screws; Set screws
    • F16B35/04—Screw-bolts; Stay-bolts; Screw-threaded studs; Screws; Set screws with specially-shaped head or shaft in order to fix the bolt on or in an object
    • F16B35/041—Specially-shaped shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L23/00—Flanged joints
    • F16L23/02—Flanged joints the flanges being connected by members tensioned axially
    • F16L23/036—Flanged joints the flanges being connected by members tensioned axially characterised by the tensioning members, e.g. specially adapted bolts or C-clamps
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S285/00—Pipe joints or couplings
    • Y10S285/92—Remotely controlled

Definitions

  • the invention relates to a remotely releasable pipe connection, in particular for nuclear plants, with two pipe ends, each of which has a flange, with a centering aid which interacts with the two flanges, with a seal and with a fastening screw for pressing the two flanges together.
  • Pipe connections of the type mentioned above are e.g. known from German Offenlegungsschriften 32 23 427, 33 40 465 and 34 31 325. There they are intended for a nuclear facility, namely for the reprocessing of spent nuclear fuel. Furthermore, a fastening screw can be found in German Offenlegungsschrift 2 258 858, which has different thread areas with the same pitch. A conical thread area merging into a cylindrical thread makes it easier to screw a nut without tilting and enables the use of remote-controlled elements for the screwing process.
  • EP-A-0116488 discloses a device for screwing in and unscrewing studs and for turning the corresponding stud nuts for the cover attachment of a nuclear reactor vessel. From this can be seen the separate arrangement of turning mechanisms for screwing and unscrewing the stud screw and turning the stud nut according to their task.
  • the aim of the invention is to improve the known connections, with the aim of simplifying the parts and thus making them easier to use. This is particularly important for nuclear facilities of the type mentioned above, in which accessibility is restricted not only in normal operation but above all for repair purposes.
  • the fastening screw has two threaded areas which become effective one after the other when pressed together, the first threaded area having a substantially greater pitch than the second threaded area.
  • the movement necessary to close the pipe connection is divided into two sections. Of these, the first section is quickly covered with the screw, because a thread with a large pitch is used. At the end of this section, the screw is in the counter flange anchored but not yet tightened to a substantial tension. The thread area with a smaller pitch is then used to generate the desired high clamping force, which is required for sealing and for the transmission of pipe bending moments. This happens on a shorter path and due to the smaller gradient with a correspondingly small torque. Since both sections of the movement required to close the connection are covered by means of a single fastening screw, it is not necessary to center several parts remotely. The "steeper" thread also prevents seizing in the nut thread of the fixed flange, so that it does not have to be interchangeable. This saves a lot of space.
  • the first thread can advantageously be a coarse thread with at least twice the pitch as the second thread of the fastening screw, which is referred to below as a fine thread.
  • the two threads can also have opposite pitch directions so that undesired turning is avoided. Since the coarse thread is used for holding while the connection is tightened with the fine thread, 200 kN screw force can be applied with ferritic screw steel, for example.
  • the coarse thread can have an axial thread play to the counter flange of at least 0.5 mm. It is preferably much larger, namely 2 mm or more. With this thread play one achieves that the threading of the fastening screw is facilitated and can therefore also be carried out by remote control, in which the fastening screw cannot be centered exactly. In addition, such a large clearance still guarantees sufficient freedom of movement between the screw and nut threads even in the event that cold welding results in an application of material.
  • the coarse thread can be rolled. This means that no complex, precise machining is necessary. In addition, rolled threads are less prone to seizure.
  • the shaft part between the two threads can advantageously be designed as an expansion shaft. It is designed with a smaller shaft diameter and absorbs settling when the screw connection is tensioned by means of elastic suspension.
  • the expansion shaft can be provided with a thickening with which the screw is centered in the flange. This facilitates the guidance when closing the screw connection. Furthermore, the thickening prevents the screw from migrating sideways under the effect of asymmetrical frictional forces in the nut.
  • a particularly advantageous embodiment of the invention consists in that the first thread engages in a threaded bore in one flange and the second thread in a threaded bore in a sleeve which is supported on the other flange.
  • the sleeve is expediently captively attached to the fastening screw.
  • the screw movement of the sleeve on the fine thread in the direction away from the coarse thread is limited by a fixed stop (collar).
  • the collar also ensures a clear starting position before the clamping process begins and enables the coarse thread to be screwed in fully.
  • the sleeve has a double internal thread that can be screwed over both the fine thread and the coarse thread.
  • the double thread enables a smaller diameter of the fine thread.
  • both threads have the same nominal outside diameter.
  • the sleeve is therefore rotated over the coarse thread, even though its inside diameter is smaller than the outside diameter of the coarse thread.
  • the coarse thread forms coarse transverse grooves in the fine thread, which is advantageous Can absorb lubricants, dirt and chips and reduce its tendency to eat.
  • the sleeve and the screw can have flat edges of different dimensions for attaching tools.
  • the number of edges of the sleeve can be greater than the number of edges of the screw.
  • the shape is particularly advantageous in that the sleeve has a hexagon, while the screw has a square.
  • a square enables a larger angle of rotation and radial play between the flat edge and the tool than a hexagon, which is advantageous for the attachment to an inclined screw. This is advantageous because the loose screw with its coarse thread must be classified first. If it is in its correct position, the tool for the sleeve nut can be pushed on with less play. It is also possible to provide the sleeve with a square and the screw with a triangle.
  • the flat edge of the screw should have a width across flats that is at least 2 mm larger than the diameter of the expansion shaft.
  • a blind hole should be provided in its center. A drill can be centered on this, which is then clamped to the flat edge and is used to drill the expansion shaft when the coarse thread is stuck.
  • a short length can be provided with a coarse internal thread, which prevents the screw from falling out when the flange is being transported. Then the screw and the sleeve can also be easily removed by remote control so that, for example, stiff screws can be replaced without removing the flange.
  • the flanges can be routinely fitted with overhauled, newly lubricated screws and sleeves.
  • other possibilities are also conceivable for fixing the fastening screw in the releasable flange. To the Example, one can proceed so that the detachable of the two flanges has an inner collar against which a slotted ring with a wedge cross section acts as a back stop for the fastening screw.
  • the pipe connection according to the invention is that at least one of the flanges is provided with projections on the edge, via which a screw prestressing force exceeding the necessary sealing force is transmitted. This ensures that the desired sealing force of the connection is not significantly exceeded, but at the same time the flanges have a rigid relative position to one another. Then the flanges can not move significantly against each other, so that the seal remains at rest.
  • the seal in the pipe connection according to the invention is advantageously a piece of pipe with curved sealing surfaces, which compensates for a radial offset.
  • the seal is preferably a double cone seal made of metal with a preferred cone angle between 35 and 60 °.
  • the seal should consist of a steel of the same type as the pipes, preferably austenite, because this is favorable for the corrosion load and also allows plastic deformations to compensate for inaccuracy with low forces. It can be fixed to one of the flanges with a locking ring.
  • the seal can also be arranged countersunk in a flange, with the result that damage to the seal during transport of the pipe pieces can be avoided.
  • a projecting sealing section can be provided on the stationary pipe end. This has the advantage that reworking, for example using an automatic welding machine or cleaning, is also possible by remote control.
  • the sealing section can also serve for centering. It can also be in the form of an interchangeable ring or an interchangeable socket be trained to enable quick remedial action in the event of damage.
  • the pipe connection according to the invention can advantageously also be used in such a way that the pipe connection is provided on each of the two sides of a fitting, with a pendulum suspension acting above the pipe connection.
  • the fittings are easily replaceable. They can be fastened with a common screw arranged between the two pipe connections, so that a particularly simple attachment is possible.
  • the pendulum movement also ensures favorable pre-centering.
  • the large fastening force of the screw in the pipe connection according to the invention also makes it possible for the screw to be arranged asymmetrically to the pipe axis in the case of a single pipe.
  • This is a significant advantage over the known pipe connections, in which several screws are provided for one pipe.
  • a flange with a reduced width e.g. a rectangular flange, in the direction transverse to the plane of an outgoing pipe bend, which is referred to as a jumper.
  • This form takes advantage of the fact that the normally vertical pipes exert temperature-related bending moments, especially in a vertical plane, so that transverse flattening of the flange does not result in a loss of strength.
  • the tubes coming from a multiple flange can advantageously be brought together in one plane and with a common one Be attached. This applies to two, three or more pipes. This enables a common expansion without dismantling neighboring pipes.
  • the screw is made of a different type of material than the flange and the sleeve in order to avoid fretting of the same type of material.
  • the screw can e.g. be formed as ferrite or martensite, the flanges made of austenite.
  • a seizure protection cap made of the screw material should be shrunk onto the sleeve, that is also preferably made of ferrite or martensite.
  • a combination tool that is particularly suitable for operating the pipe connection is designed with two rotating mechanisms located in a common housing and a concentrically arranged screw sleeve and nut sleeve for transmitting the respective rotary movement to the screw and / or nut so that a first rotating mechanism for actuating the screw and sleeve Coarse thread is provided, the screw and sleeve rotates together, and that a second turning mechanism then only rotates the sleeve and the second turning mechanism is supported against the screw. This avoids impermissible torques on the flanges even with large screw torques.
  • Instrumentation of the slewing gear can be used to determine the number of revolutions or the running time in order to put the combination tool out of operation after the pipe connection has been closed or opened. Furthermore, the torque are determined, preferably by measuring the active power in a three-phase asynchronous motor. This makes it possible to immediately identify stiff screws and replace them before they start to seize.
  • an impact wrench effect can also be provided, which is effective when moving in the direction of loosening the coarse thread, and advantageously only when an adjustable normal torque is overwritten. This also enables loosening of coarse threads.
  • the possible torque of the combination tool can be adjustable in stages, above all by limiting the current in the asynchronous motor. Low torques are e.g. desirable when picking up the fastening screw and threading into the coarse thread.
  • the speed of the slewing gear can also be made adjustable, e.g. to have the lowest possible relative speed when centering or to achieve faster operation with small screws with low torques than with large screws which have to be actuated with correspondingly large forces.
  • a programmed step sequence control can also be provided, which stops the slewing gear and gives a signal when the torque rises prematurely. This indicates that there is a problem with the mounting screw that requires special measures.
  • a key hexagon nut
  • square nut key for the screw.
  • the hexagon nut should act as a funnel and make it easier to thread the square screw.
  • the hexagon socket provided with less play can then be advanced over the sleeve, preferably at a reduced speed and with a low torque in the opposite direction. After being attached, the sleeve is then tensioned in the forward direction with great torque.
  • the pipe connection 1 according to FIGS. 1, 2 and 3 comprises a fixed pipe end 2 which is seated in a fixed flange 3 which is flattened in a straight line on the sides, as shown in FIG.
  • the pipe end 2 is welded to a pipe 4 on the side facing away from the pipe connection 1.
  • the pipe end 2 widens to form a collar 5 which is supported on the flange 3.
  • the collar 5 is tapered at its free end outside and inside, so that conical surfaces 6 and 7 are formed.
  • the cone angle is about 30 ° in each case.
  • the outer conical surface 6 serves to guide the counterpart 9 when the pipe connection is closed, while the inner conical surface 7 is designed as a contact for a sealing body 10.
  • the counterpart 9 is a bend that is welded to the flange 12 as the other pipe end 11.
  • the flange 12 engages with a cylindrical recess 13 over the collar 5.
  • the cylindrical recess 13 tapers on the side facing away from the flange 3 to a conical region 14 which, like the conical region 7, has an angle of 30 ° and forms a second abutment for the sealing body 10.
  • a threaded bore 16 with a coarse thread is provided in the flange 3, into which a screw 17 engages, which will be described later with reference to FIGS. 6 and 7.
  • the screw 17 also extends through a bore 20 in the flange 12, which has several sections.
  • the last area 23 is also cylindrical with a slightly smaller diameter. Between the sections 21, 22 and 23, in particular on the outer sides of the flange 12, bevels with 45 ° or less are provided.
  • a clamping sleeve 25 On the screw 17 is a clamping sleeve 25, which has a threaded bore 26.
  • the thread is designed both as a fine thread and as a coarse thread, as will be explained in more detail later with reference to FIGS. 10.
  • the sleeve 25 is supported on a plate 28 with a raised edge 29 on the side of the flange 12 facing away from the flange 3.
  • the side 30 of the flange 12 facing the flange 3 has a collar acting as a spacer 31 at the edge.
  • two hooks 33 are pressed into the upper side of the flange 12, which, as shown in FIG. 2, can be placed on the upper curve of the flange 3. With the hook 33, the loose flange 12 is supported and centered on the fixed flange 3 so that the screw 17 can be screwed into the threaded bore 16.
  • the pipe connection 1 When the screw 17 is completely screwed in, the pipe connection 1 has the position shown in FIG. Then the sleeve 25 is tightened with the thread 26 until the collar 31 abuts the flange 3. The pipe connection 1 then assumes the operating position shown in FIG. 3. In this position, the sealing body 10 is deformed so that the tightness of the pipe connection 1 is ensured, and the spacer 31 lies firmly on the counter flange 3. Further rotation of the sleeve 25 then leads to a considerable increase in the torque required for this, so that the termination of the closing movement can be easily detected.
  • the screw 17 shown to scale in FIG. 6 has a length L of 270 mm. It has a square head 40 at the right end, which has a width across flats of 30 mm and ends with a truncated cone 41 towards the free end 42. The cone angle is 60 °. A central blind bore 43 is provided in the square 40.
  • the square 40 which makes up about a fifth of the screw length L, is adjoined by a collar 44 widened to a diameter of 38 mm, which is delimited by two conical surfaces at 30 or 60 ° relative to the screw axis.
  • the neighboring one cylindrical section 45 has a diameter of 30 mm at a length of approximately 10 mm. It forms an outlet for a thread 46, which is designed both as a coarse thread and as a fine thread.
  • the thread 46 is shown in detail in FIG 10 on a larger scale.
  • the length of the threaded section 46 is approximately a quarter of the screw length L.
  • the expansion shaft 48 On the left side of the thread 46 is a screw part 48, which is designed as an expansion shaft.
  • the expansion shaft 48 has a diameter of 25 mm and a length of about 40 mm. It passes with a conical surface 49, which has a conical angle of 15 °, to a thickened guide cylinder 50 with a diameter of 30 mm, which directly adjoins the thread 46.
  • a second thread area 52 of the screw 17, which adjoins the expansion shaft 48, has a rolled coarse thread, which is shown on a larger scale in FIG.
  • the length of this threaded area 52 is 40 mm, about a seventh of the screw length L.
  • the other end 53 of the screw 17 is formed by a truncated cone 54 with a cone angle of 20 °, which starts from a short cylindrical section 55 with a diameter of 24 mm and is used to thread the screw 17 into the threaded bore 16.
  • the clamping sleeve 25 shown in FIGS. 8 and 9 has an externally cylindrical section 58 and an adjoining hexagon 59 which has a wrench size of 46 mm and is flattened on the side facing away from the cylindrical section 58 to form a truncated cone 60 at an angle of 30 °.
  • the sleeve 25 contains about 50 mm in length in the area of the hexagon 59, the thread 26, which is designed as a coarse and fine structure, as shown in more detail in FIG 10.
  • the remaining section 61 of the total length of approximately 80 mm, that is to say a length of approximately 30 mm, is cylindrical with an inner diameter that is 37 mm slightly larger than the outer diameter of the thread 26.
  • FIG. 11 shows the coarse thread 52 of the screw 17 on a scale enlarged ten times. It has a groove base 64 rounded with a radius of 1.9 mm and an internal thread diameter of 26.4 mm. The flank angle ⁇ is 60 °. The depth T of the threads is 4.1 mm. The pitch 65 of the right-hand thread 52 is 8 mm. FIG. 11 also shows that there is considerable play with respect to the nut thread, as is provided in the threaded bores 16 and 26. The game labeled S is more than 1 mm.
  • the fine thread 46 engages in the thread 26 of the sleeve 25, which is adapted to both the coarse thread 52 and the fine thread 46. Since the fine thread is cut to the left, the coarse thread 52, on the other hand, to the right, there are cavities and grooves in the thread area that can absorb lubricants, as well as abrasion and dirt that occurs when the threads are actuated. This reduces the thread's susceptibility to faults.
  • FIG. 12 shows in a section transverse to the pipe axis the ring 60 made of spring material, which serves to hold the sealing body 10, as is provided in the pipe connection according to the invention.
  • the sealing body 10 in the undeformed state has two approximately cylindrical inner wall regions 62 and 63 which are separated from one another by a round groove 64 in the inner wall of the sealing body 10.
  • a round groove 64 in the inner wall of the sealing body 10.
  • two ribs 66 In the area of the round groove 64, on the outside of the sealing body 10 there are two ribs 66 and which run at right angles to the pipe axis around the circumference of the sealing body 10 67 are provided, which are arranged at a distance from one another.
  • the ring 60 In the space 68 between the ribs 66, 67 engages the retaining ring 60, which is blown into a groove 69 in the loose flange 12. As shown in FIG. 12, the ring 60 is slotted at 70. The ends 71 and 72 facing the slot 70 are provided with hook-shaped recesses 73 and 74. Therefore, the ring 60 can be gripped there with a pliers tool and pulled together. Its decreasing diameter allows it to be lifted out of the groove 69. In normal operation, however, the ring 60 engages in the intermediate space 68 between the ribs 66 and 67 with the thickenings 71 and 72 and with further projections 75 which are evenly distributed around the circumference of the sealing body 10. To simplify the sealing ring 10, one of the ribs, namely the rib 66 facing the counter flange 3, can be omitted.
  • FIGS. 13 and 14 show an embodiment in which the loose flange 12 ⁇ is connected to a pair of hooks 81 via a U-shaped bracket 80.
  • the hooks are provided with a common web 82 on which two disks 83 and 84 determine an engagement point 85 for a gripper.
  • the hooks 81 engage over a support tube 87 which is fastened to the fixed flange 3 ⁇ with two supports 86.
  • the fixed flange 3 ⁇ comprises two pipe connections 1 ⁇ with the pipe ends 2 ⁇ on one side.
  • the pipe ends 2 ⁇ are welded to a socket 88 of the fixed flange 3 ⁇ .
  • the fixed flange 3 ⁇ with a projection 89 corresponding to the collar 5 with the outer cone 6 ⁇ forms a centering possibility for the loose flange 12 ⁇ .
  • the inner cone 7 ⁇ gives the contact surface for the sealing body 10 ⁇ .
  • the other pipe ends 11 ⁇ lead to a ball valve 90, which is actuated with a lever 91 between the positions on and off can be.
  • the ball valve 90 can be replaced after loosening the screw 17 ⁇ .
  • the fastening screw 17 ⁇ is supported in this embodiment according to FIGS. 13 and 14 with a shell 94 which is fastened with screws 95 and flanges 96 to the loose flange 12 ⁇ .
  • the screw 17 ' is held so that after loosening, even with pivoting movements which can be exercised around the holding rod 87 as a fulcrum, it does not lose the horizontal position favorable for threading into the fixed flange 3'.
  • the combination tool 100 shown in FIGS. 15 to 18 comprises, as a wrench, a screw sleeve 101 (square nut) that engages the screw 17 and a nut sleeve 102 (hexagon nut) that is assigned to the sleeve 25 and is concentric to the sleeve 101.
  • the screw sleeve 101 is connected directly to a shaft 104 which is mounted in the housing 105 of the tool 100 with a needle bearing 106 at one end and 107 at the other end.
  • a ball bearing 108 which rests with a guide body 109 on a collar 110 of the shaft 104, serves for the axial fixing.
  • a rotating mechanism 103 which consists of a three-phase asynchronous motor 112 and a gear 113, engages on the shaft end 111 projecting from the housing 105.
  • the motor 112 can be reversed for clockwise and anti-clockwise rotation.
  • the nut sleeve 102 is seated with a sliding wedge connection 114 on a hollow shaft 115 which concentrically surrounds the shaft 104.
  • the hollow shaft 115 has an external toothing 116 at its end facing away from the nut sleeve 102.
  • the hollow shaft 115 is supported in the housing 105 via two roller bearings 117 and 118.
  • a pinion 120 engages in the toothing 116 and is mounted in an extension 121 of the housing 105 shown offset by 90 °.
  • the pinion shaft 122 leads to a rotating mechanism 123 for rotating the nut sleeve 102.
  • the rotating mechanism 123 also includes a gear 124 and a three-phase asynchronous motor 125 with clockwise and anti-clockwise rotation, so that the nut sleeve 102 can be rotated in both directions.
  • the nut sleeve 102 has at its end facing away from the hexagon socket 124 on the outside a groove 128.
  • a pin 126 engages therein, which is fastened to a slide 130 guided in the housing 105 .
  • the carriage 130 has a toothing 129 on its underside which meshes with a pinion 131.
  • the pinion 131 is connected to a bevel gear 133 via a shaft piece 132. With this, as can be seen in FIG. 15, a bevel gear 134 meshes, the drive shaft 135 of which leads out of the housing 105.
  • the drive shaft 135 leads to a third rotating mechanism 137 with a gear 138 and a reversible electric motor 139, with which the nut sleeve 102 can be adjusted in the direction of the drive shaft 104.
  • 15 shows the most extended position of the nut sleeve 102. In this position it can include the sleeve 25.
  • the retracted position is drawn at 102 '.
  • the nut sleeve 102 forms a funnel-shaped extension of the conical widening 137 of the screw sleeve 101, so that the placement of the tool 100 on the screw 17 is facilitated.
  • the large torque of, for example, 800 Nm required for tightening the expansion screw 17 then acts directly between the screw sleeve 101 (4-point nut) and the nut sleeve 102 (6-point nut), so that no larger torques from the housing 105 into the tool 100 or must be transferred to the fixed flange 3.
  • the combination tool 100 is constructed asymmetrically in that the motors 125 and 139 are arranged on one side (left) next to the center of the shaft 111 of the screw sleeve 101. This results in a reduced approach dimension on one side (right) of the flange screws arranged around a pipe.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Flanged Joints, Insulating Joints, And Other Joints (AREA)
  • Mutual Connection Of Rods And Tubes (AREA)
  • Hand Tools For Fitting Together And Separating, Or Other Hand Tools (AREA)
  • Earth Drilling (AREA)
  • Joints With Pressure Members (AREA)

Claims (37)

  1. Raccord de tuyau démontable par télécommande, notamment pour des installations de génie nucléaire, comprenant deux extrémités de tuyau, qui comportent chacune une bride, des moyens auxiliaires de centrage qui coopèrent avec les deux brides, un dispositif d'étanchéité et une vis de fixation destinée à presser les deux brides l'une contre l'autre, caractérisé en ce que la vis de fixation (17) a deux tronçons filetés (46, 52), qui entrent en action l'un après l'autre lorsque les deux brides sont pressées l'une contre l'autre, le premier tronçon fileté (52) ayant un pas sensiblement plus grand que le second tronçon fileté (46).
  2. Raccord de tuyau suivant la revendication 1, caractérisé en ce que le premier filetage (52) a un filetage grossier ayant un pas au moins deux fois plus grand que le second filetage (46) de la vis de fixation (17).
  3. Raccord de tuyau suivant la revendication 1 ou 2, caractérisé en ce que les deux filetages (46, 52) ont des pas de sens inverse.
  4. Raccord de tuyau suivant la revendication 2 ou 3, caractérisé en ce que le filetage grossier (52) a un jeu de filetage (S) axial par rapport à la contre-bride (3), d'au moins 0,5 mm et, de préférence, d'au moins 2 mm.
  5. Raccord de tuyau suivant l'une des revendications 2 à 4, caractérisé en ce que le filetage grossier (52) est enroulé.
  6. Raccord de tuyau suivant l'une des revendications 1 à 5, caractérisé en ce que la partie de tige comprise entre les deux filetages (46, 52) est constituée sous la forme d'une tige allégée (48).
  7. Raccord de tuyau suivant la revendication 6, caractérisé en ce que la tige allégée (48) est épaissie sur un tronçon partiel (50) à proximité du filetage fin (46), en vue du centrage de la vis (17) dans la bride (12).
  8. Raccord de tuyau suivant l'une des revendications 1 à 7, caractérisé en ce que le premier filetage (52) se visse dans un trou taraudé (16) de l'une des brides (3) et le second filetage (46) se visse dans un trou taraudé (26) d'une douille (25) qui s'appuie sur l'autre bride (12).
  9. Raccord de tuyau suivant la revendication 8, caractérisé en ce que le vissage de la douille (25) sur le filetage fin (46) est limité dans le sens s'éloignant du filetage grossier (52) par une butée (44) fixe.
  10. Raccord de tuyau suivant la revendication 8, caractérisé en ce que la douille (25) a un double taraudage (26) qui peut se visser aussi bien sur le filetage mince (46) que sur le filetage grossier (52).
  11. Raccord de tuyau suivant l'une des revendications 8 à 10, caractérisé en ce que la douille (25) et la vis (17) présentent des pans (40, 59) de dimension différente pour la mise en place d'outils (100).
  12. Raccord de tuyau suivant la revendication 11, caractérisé en ce que le nombre de pans de la douille (25) est supérieur au nombre de pans de la vis (17), notamment sous la forme d'un six-pans/quatre-pans (59,40).
  13. Raccord de tuyau suivant la revendication 6 et 11 ou 12, caractérisé en ce que le pan (40) de la vis (17) a un surplat qui est supérieur d'au moins 2 mm au diamètre de la tige allégée (48), et en ce qu'il est prévu un trou borgne (43) au centre du pan (40).
  14. Raccord de tuyau suivant l'une des revendications 1 à 13, caractérisé en ce qu'il est prévu, dans la bride (12) amovible, un court tronçon ayant un taraudage (21) grossier qui empêche la vis (17) de tomber lors du transport de la bride (12).
  15. Raccord de tuyau suivant l'une des revendications 1 à 13, caractérisé en ce que celle des deux brides qui est amovible comporte un épaulement intérieur sur lequel une bague fendue de section transversale cunéiforme agit en tant que butée arrière pour la vis de fixation (17).
  16. Raccord de tuyau suivant l'une des revendications 1 à 15, caractérisé en ce qu'au moins l'une des brides (3, 12) est munie, sur le bord, de saillies (31) par lesquelles est transmise une force de précontrainte de vissage dépassant la force d'étanchéité qui est nécessaire.
  17. Raccord de tuyau suivant l'une des revendications 1 à 16, caractérisé en ce que le dispositif d'étanchéité est une pièce tubulaire (10) à surface d'étanchéité arquée, qui compense un décalage radial.
  18. Raccord de tuyau suivant l'une des revendications 1 à 17, caractérisé en ce que le dispositif d'étanchéité est un dispositif d'étanchéité à double cône (10) en métal.
  19. Raccord de tuyau suivant l'une des revendications 1 à 18, caractérisé en ce que le dispositif d'étanchéité (10) est fixé par un jonc élastique (60) à l'une des brides (3, 12).
  20. Raccord de tuyau suivant l'une des revendications 1 à 19, caractérisé en ce que le dispositif d'étanchéité (10) est noyé dans une bride (12).
  21. Raccord de tuyau suivant l'une des revendications 1 à 20, caractérisé en ce qu'il est prévu une partie d'étanchéité (6) en saillie à l'extrémité du tuyau (2) qui est fixe.
  22. Raccord de tuyau suivant la revendication 21, caractérisé en ce que la partie d'étanchéité (6) sert au centrage.
  23. Raccord de tuyau suivant l'une des revendications 21 ou 22, caractérisé en ce que la partie d'étanchéité est un anneau remplaçable ou une douille remplaçable.
  24. Raccord de tuyau suivant l'une des revendications 1 à 23, caractérisé en ce que le raccord de tuyau (1) est prévu des deux côtés d'un robinet (90), et en ce qu'une suspension pendulaire (81, 87) est prévue au-dessus du raccord de tuyau (1).
  25. Raccord de tuyau suivant la revendication 24, caractérisé en ce que les deux raccords de tuyau (1) ont une vis (17") commune disposée entre eux.
  26. Raccord de tuyau suivant l'une des revendications 1 à 23, caractérisé en ce que plusieurs raccords de tuyau (1) sont munis d'une bride (3, 12) commune, et en ce que la vis (17) est disposée entre les axes des tuyaux.
  27. Raccord de tuyau pour un tuyau individuel suivant l'une des revendications 1 à 23, caractérisé en ce que la vis (17) est disposée dissymétriquement par rapport à l'axe du tuyau.
  28. Raccord de tuyau suivant l'une des revendications 1 à 27, caractérisé en ce qu'il est prévu une bride de moindre largeur (par exemple une bride rectangulaire) dans la direction perpendiculaire au plan d'un coude de tuyau (11) partant.
  29. Raccord de tuyau suivant l'une des revendications 1 à 26, caractérisé en ce qu'à partir d'une bride (12) multiple, plusieurs tuyaux (11) partant sont réunis dans un plan et sont reliés à un collier commun de suspension.
  30. Raccord de tuyau suivant l'une des revendications 8 à 29, caractérisé en ce que la vis (17) est en un matériau d'un autre type que la bride (3) et la douille (25), et en ce que sur la douille (25) est posé, en étant de préférence fretté, un capot en le matériau de la vis destiné à protéger du grippage.
  31. Outil universel destiné à télécommander le raccord de tuyau suivant la revendication 8, caractérisé en ce qu'il est prévu un premier dispositif de rotation (103) pour le filetage grossier (152) en vue de faire tourner ensemble la vis (17) et la douille (25), en ce qu'il est prévu un second dispositif de rotation (123) destiné à faire tourner la douille (25) seule, en ce que le second dispositif de rotation (123) s'appuie, lors de la rotation de la douille (25), sur la vis (17), et en ce que le premier dispositif de rotation (103) et le second dispositif de rotation (123) se trouvent dans ou sur un bâti (105) commun de l'outil (100) et transmettent le mouvement de rotation par une douille filetée (101) et par une douille en forme d'écrou (102) qui sont disposées concentriquement l'une à l'autre.
  32. Outil universel suivant la revendication 31, caractérisé en ce que par une instrumentation des dispositifs de rotation (103, 123) la vitesse de rotation ou la durée de fonctionnement ou le couple sont déterminés de préférence en mesurant la puissance efficace dans le cas d'un moteur asynchrone (112, 125) à courant triphasé.
  33. Outil universel suivant la revendication 31 ou 32, caractérisé en ce qu'il est prévu un effet de tournevis à frappe dans le premier dispositif de rotation (103) dans le sens du dévissage du filetage grossier (52), qui devient efficace après dépassement d'un couple normal réglable.
  34. Outil universel suivant l'une des revendications 31 à 33, caractérisé en ce que le couple qui est possible peut être réglé par palier, notamment en limitant le courant du moteur (112, 125) et, le cas échéant, la vitesse de rotation des dispositifs de rotation (103, 123).
  35. Outil universel suivant l'une des revendications 31 à 34, caractérisé en ce qu'une clé (102) pour la douille (125) peut être déplacée axialement par rapport à la clé (101) pour la vis (17).
  36. Outil universel suivant l'une des revendications 31 à 35, caractérisé en ce qu'il est prévu une commande séquentielle pas-à-pas programmée qui arrête les dispositifs de rotation (103, 123) et émet un signal en cas d'augmentation prématurée d'un couple.
  37. Outil universel suivant l'une des revendications 31 à 36, caractérisé par une dimension radiale sensiblement plus petite d'un côté de l'axe de la vis que du côté opposé.
EP88110663A 1987-07-15 1988-07-04 Raccord de tuyau télémanipulable et outil multifonctionnel pour celui-ci Expired - Lifetime EP0299324B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3723386 1987-07-15
DE19873723386 DE3723386A1 (de) 1987-07-15 1987-07-15 Fernbedient loesbare rohrverbindung und kombinationswerkzeug dafuer

Publications (2)

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EP0299324A1 EP0299324A1 (fr) 1989-01-18
EP0299324B1 true EP0299324B1 (fr) 1991-11-21

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EP88110663A Expired - Lifetime EP0299324B1 (fr) 1987-07-15 1988-07-04 Raccord de tuyau télémanipulable et outil multifonctionnel pour celui-ci

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US (1) US4953580A (fr)
EP (1) EP0299324B1 (fr)
JP (1) JPS6430991A (fr)
DE (2) DE3723386A1 (fr)

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3908476A1 (de) * 1989-03-15 1990-09-20 Wiederaufarbeitung Von Kernbre Drehschrauber
JPH07186126A (ja) * 1993-12-27 1995-07-25 Toyota Kihan:Kk 型枠締結用ねじ部材の締緩装置
JP2791279B2 (ja) * 1994-06-08 1998-08-27 山本窯業化工株式会社 堆積岩割り肌状凹凸模様を有する装飾材の製造方法
NO308329B1 (no) * 1999-01-28 2000-08-28 Den Norske Metallpakningsfabri Tetningsarrangement
NO320661B1 (no) * 2002-05-10 2006-01-16 Advanced Prod & Loading As Anordning for sammenkoblinger av rorledninger
US7591485B2 (en) * 2005-07-11 2009-09-22 Simmons Tom M Connections for tubing and method of connecting tubing segments
DE102010014318A1 (de) * 2010-04-09 2011-10-13 Siemens Aktiengesellschaft Befestigungseinrichtung zum kraftschlüssigen Verbinden zweier Werkstücke sowie Verwendung einer Befestigungseinrichtung
US8602390B2 (en) * 2010-11-30 2013-12-10 General Electric Company Jacking mechanism
CN104339155B (zh) * 2014-10-31 2016-08-31 金盛紧固技术(安徽)有限责任公司 喉箍螺钉半自动装配机
FR3053519B1 (fr) * 2016-06-30 2018-08-10 Agence Nationale Pour La Gestion Des Dechets Radioactifs Procede de formation et d'installation in situ d'un double tubage d'une alveole de stockage souterrain de dechets radioactifs
KR102343225B1 (ko) * 2018-08-09 2021-12-27 한온시스템 주식회사 냉매 피팅용 열 순환 저항 체결 시스템
US11607929B2 (en) * 2018-08-09 2023-03-21 Hanon Systems Thermal cycle resistant fastening system for refrigerant fitting
EP3660242B1 (fr) * 2018-11-29 2023-08-02 General Electric Company Connexion de boulon pour relier deux brides
CN113294615B (zh) * 2021-05-26 2022-09-06 河北岳丰管件产业技术研究有限公司 一种弯头拼接块及弯头组件

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1497497A (en) * 1921-09-13 1924-06-10 Gapp John Superheater-tube connection
US1852279A (en) * 1929-05-16 1932-04-05 Superheater Co Ltd Means for securing tubes to headers
US2423762A (en) * 1942-05-15 1947-07-08 Everett Samuel James Pipe joint
DE1252483B (de) * 1962-02-01 1967-10-19 Aktiebolaget Atomenergi Stockholm Flanschverbindung fur Druckbehälter oder Rohre mit abwechselnd in entgegengesetzter Richtung geneigten Spannschrauben
DE2258858A1 (de) * 1972-12-01 1974-06-06 Masch Und Bohrgeraete Fabrik Schraube
US4200312A (en) * 1978-02-06 1980-04-29 Regan Offshore International, Inc. Subsea flowline connector
US4603889A (en) * 1979-12-07 1986-08-05 Welsh James W Differential pitch threaded fastener, and assembly
DE3223427A1 (de) * 1982-06-23 1983-12-29 Kernforschungszentrum Karlsruhe Gmbh, 7500 Karlsruhe Kupplung zum gleichzeitigen verbinden mehrerer, eng benachbarter rohrleitungen
FR2540279A1 (fr) * 1983-01-28 1984-08-03 Kley France Appareil de vissage-devissage, en particulier pour visser-devisser les goujons de fixation du couvercle de la cuve d'un reacteur nucleaire
DE3340465C2 (de) * 1983-11-09 1986-07-03 Deutsche Gesellschaft für Wiederaufarbeitung von Kernbrennstoffen mbH, 3000 Hannover Rohrleitungsverbindungsvorrichtung zum Verbinden von ortsfesten Rohrleitungsanschlüssen
DE3431325A1 (de) * 1984-08-25 1986-03-06 Deutsche Gesellschaft für Wiederaufarbeitung von Kernbrennstoffen mbH, 3000 Hannover Zentrier- und hantierungshilfe fuer zusammenkuppelbare rohrleitungsflansche
LU85982A1 (fr) * 1985-06-28 1986-07-17 Euratom Raccord telemanipulable entre une bride fixe et une bride mobile

Also Published As

Publication number Publication date
JPS6430991A (en) 1989-02-01
EP0299324A1 (fr) 1989-01-18
DE3723386A1 (de) 1989-01-26
DE3866296D1 (de) 1992-01-02
US4953580A (en) 1990-09-04

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